Milling machine



Nov. 22, 1949 E. G. ROEHM ETAL 2,489,227

MILLING MACHINE Filed Oct. 5, 1942 e Sheets-Sheet 1' INVENTOR. fRu/HG Hoff/M BY 2 flay/$ 3424 ATTORNEY.

Nov. 22, 1949 E. G. ROEHM ETAL MILLING MACHINE Filed Oct. 3, 1942' 6 Sheets-Sheet 5 mwN WWN M H d MW WM f Nov. 22, 1949 E. G. ROEHM ETAL MILLING MACHINE 6 Sheets-Sheet 4 Filed Oct. 5, 1942 INVENTOR. fww$ 1%EHM N5 FAfTSCV/l /47' ENE) Patented Nov. 22, 1949 MILLING MACHINE Erwin G. Roehm, Norwood, and Hans Fritschi, Silver-ton, Ohio, assignors to The Cincinnati Milling Machine Co., Cincinnati, Ohio, a corporation of Ohio Application October 3, 1942, Serial No. 460,706

31 Claims.

This invention relates to machine tools and more particularly to improvements in milling machines.

One of the objects of this invention is to provide an improved automatic milling machine which may be selectively controlled to provide fast, slow or automatically variable feed rates and automatic separation between cutter and work after a milling operation.

Another object of this invention is to provide an improved variable feed transmission for a milling machine which will produce a constant feeding rate between the cutter and work.

A further object of this invention is to provide improved means for automatically adjusting and maintaining a selected feed rate constant and which may be utilized as part of a variable feed control.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the accompanying drawings forming a part thereof and it is to be understood that any modifications may be made in the exact structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

Referring to the drawings in which like reference numerals indicate like or similar parts:

Figure 1 is a front elevation of a machine tool embodying the principles of this invention.

Figure 2 is a diagrammatic view of the table transmission control mechanism.

Figure 3 is a diagrammatic view of the hydraulic control mechanism for the table transmission and including the interlock control for the spindle transmission.

Figure 4 is an enlarged detail view of the variable feed control attachment as viewed from the front of the machine.

Figure 5 is a section taken on the line 55 of Figure 4.

Figure 6 is a detail section on the line B6 of Figure 4.

Figure 7 is a plan view of the trip control plungers and the trip dogs for operating the same as viewed on the line '!'i of Figure 3.

Figure 8 is a section showin the trip control 4 plungers and trip dogs in elevation as viewed on the line 88 of Figure 1.

Figure 9 is a section on the line 9--9 of Figure 8 showing the adjustable delay valves for the reversing mechanism.

Figure 10 is a section on the line l0l0 of Figure 8 showing the delay pilot valves.

Figure 11 is a detail plan view of the rate control dial as viewed on the line i I| of Figure 4.

Figure 12 is a View in elevation with parts broken away of the rate and direction table control lever as viewed on line lZ-l 2 of Figure 1.

Figure 13 is a section on the line i3--l3 of Figure 12.

Figure 14 is a section on the line I4M of Figure 13.

Referring to the drawings, Figure 1 shows a front View of a machine embodying this invention and from this figure it will be noted that the machine is of the bed type comprising a bed it? upon the top of which is formed guideways I i which support a table I2 for horizontal movement; and a column or headstock is which is integrally connected to the bed and provided with guideways M formed on one face thereof. for receiving a spindle carrier l5 which is vertically movable with respect to the top of the table I2.

Briefly, the spindle carrier has a quill li'i which is slidably mounted in the carrier for horizontal adjustment and a cutter spindle H is journaled within the quill for axial movement thereby.

The transmission mechanism for traversing the table is shown diagrammatically in Figure 2. A table lead screw is is fixedly supported against rotation to opposite ends of the table as shown at 59. A rotating nut construction, indicated generally by the reference numeral 20, is anti-frictionally supported in the bed Iii and in surrounding relation to the screw. The nut construction is of the backlash eliminating type, and may be the same as that shown in copending application, Serial No. 405,354, filed in the United States Patent Ofiice on August 4, 1941 now Patent No. 2,320,353, issued June 1, 1943. Since it does not constitute any part of the present invention, detailed description thereof is not believed to be necessary. Suffice it to say that this nut construction has a driving gear.

2! which is driven from a gear 22 through a pair of intermediate idler gears 23 and 2%, whereby rotation of the nut assembly will effect axial. movement of the screw. The gear 22 integrall attached to a shaft 25 upon which a cevel gear 26 is supported for free rotation. The gear 2% may be power driven and is connectable to the shaft 25 through a shiftable clutch member 21 which is splined at 28 to the shaft 25.

A shifter fork 29 is attached to a slidable plunger 3!! which is continuously acted upon by a spring 3i to maintain the clutch out of engagement with the gear.

The plunger 30 is slidably supported in bores 32 and 33 formed in a fixed part of the bed and the plunger 30 is reduced at 3 to form a piston and cylinder to which hydraulic pressure may be admitted to effect shifting of the plunger and corn sequent engagement of the clutch.

The power for driving'the transmission is derived from a prime mover such as an electric motor 35 which has a multiple groove pulley 36 attached to its armature shaft 31. This pulley is connected b multiple V-belts 38 to a driven pulley 39 which is anti-frictionally supported in the bed for driving a pair of gears 49 and 4!.

The gear 60 drives directly 9. gear 42 which may be termed the rapid traverse drive gear. This gear is connectable through clutch means 43 to a gear pair 44 and 45. The gear 44 meshes directly with a gear 45 for driving the same in one direction and the gear 45 is connected through an intermediate idler 4'! to a second gear 68 for driving the same in an opposite direction with respect to the gear 46, the two gears 46 and 48 being supported for free rotation on a common shaft 49. The gear 45 may be connected by clutch means 59 for rotation of a, beveled gear 51 in one direction, this bevel gear intermeshing with the previously mentioned bevel gear 26. The gear 48 may be operatively connected through clutch means 52 for rotation of bevel gear in the other direction whereby the bevel gear 26 may be rotated in opposite directions to effect re ciprocation of the table. It will thus be apparent that the clutches 5B and 52 constitute direction determining clutches while the clutch t3 constitutes a rapid traverse selector clutch.

The feed transmission derives its power from a hydraulically operated motor 53 which has a drive gear 54 that is connected by a gear train 55 to a gear 56. supported for free rotation relative to a supporting shaft 51. The hydraulic motor is supplied with operating fluid through a pair of channels 58 and 58 by a hydraulic pump 60 that is driven by the prime mover 35. In other words. a gear train comprising a gear 6! which intermeshes with the gear ll and spur gears 62 and 63 connect the gear i! through a pair of bevel gears 64 to the pump drive. shaft 65. It will now be seen that the pump 60 is continuously driven by the electric motor 35 at a constant rate and that the pump in turn effects continuous operation of the hydraulic motor 53 and thereby of the gear 56.

The hydraulic motor 53 is a variable displacement motor which may be of the wobble plate type such as that shown in patent to Thoma, No. 1,931,969, having an angularly adjustable cylinder block 56 for varying its displacement and thereby its speed. The angular position of the cylinder block is controlled by a displacement control valve 6? having pressure ports 68, exhaust ports 69, and intermediate ports and it! which are connected by channels H and 1 I respectively to a fixed cylinder '52 containing a piston 13 that is connected to the block by a pin, it. The valve plunger 6'! has annular grooves which are of such width that the pressure and exhaust ports are closed when the plunger is in a central position. If the valve plunger is moved upward as viewed in Figure 2, pressure is admitted to the line H, causing decrease in motor displacement equivalent to increase in speed, while if the valve plunger is moved downward pressure is admitted to line H causing increase in motor displacement and decrease in speed. By means of this valve the displacement of the motor may be varied and thereby the speed of rotation of the gear 56.

The gears 44 and 45 which, as previously described, may be driven at a rapid traverse rate by engagement of the rapid traverse clutch 43 may also be driven at a variable feed rate upon engagement of a feed clutch 1-5 which serves to operatively connect these gears to a shaft 11 having a gear l8 which intermeshes with a. gear 19 attached to the end of shaft 51. This shaft is driven at Variable rates through a differential mechanism comprising a gear 80 which is rotatably mounted on a cross shaft 8! carried by the shaft 51 and a pair of differential gears 82 and 83. The gear 88 is connected to the gear 56 by an intervening sleeve 84 which is supported for free rotation relative to the shaft 51. The gear 82 is connected by a sleeve 85 to a gear as which is driven through a branch train from the gear 65 which is continuously driven by the electric motor 35. In other words, the gear 5| is integral with a gear 8'! and this gear is connected through intermediate idler gears 88 and 89 to the gear 86. It will now be apparent that the electric motor drives the gear 82 at a constant rate and the gear 83 at a variable rate through the pumpmotor combination.

The gearing connections are such that the gears 82 and 33 are rotated in opposite directions with the result that if they both rotate at the same speed there will be no differential action to cause bodily movement of gear 88 in spite of its rotation and therefore the shaft 5'! will remain stationary. This is equivalent to zero feed rate of the table.

Variable feed rates are obtained by increasing the rate of rotation of the bevel gear 83 above that of the gear 82 in a stepless fashion through speed variance of the hydraulic motor 53. This means that the motor has a minimum rate of rotation for zero feed rate because it must drive the gear 83 at the same rate as gear 82 as previously explained for Zero feed rate.

The angular position Of the motor cylinder block 55 for Zero feed rate is indicated b the axis 96. As the cylinder block is swung counterclockgwise from this axis the rate of rotation of gear 54 is increased until the axis 9| is reached which indicates the position of the cylinder block for producing the maximum feed rate.

A rate determining and speed matching mechanism is provided in connection with the motor and operates to select a desired rate of feed and then to automaticall maintain that rate regardless of the resistance of the cutting operation being performed by the machine. This mechanism is coupled in parallel with the differential mechanism and comprises a rate determining mechanism consisting of a large friction plate 82 and a friction roller 93, the friction roller being supported on a spline shaft 94 for radial adjustment with respect to the plate. The spline shaft is driven from the constant speed gear 61 through shaft 95, bevel gearing 95 and spur gearing 91.

The friction disc is connected by a shifter fork 98 to a rack 99 that intermeshes with a rotatable pinion loll. Rotation of the pinion moves the friction roller radially of the plate 92 and it will be obvious that when the friction roller is near the center of the plate it Will rotate the plate at a relatively fast rate and When shifted to the periphery of the plate it will rotate it at a relatively slow rate.

The plate is formed integral with a shaft IOI which is supported on an anti-friction thrust bearing I02 and this thrust bearing is mounted in a slidable sleeve I03 whereby the plate may be continuously urged by a spring I04 into frictional engagement with the roller 93. The spring is interposed between an internal annular flange i135 formed on the sleeve and a fixed plate I06 forming the bottom of a bore I01 formed in a. fixed part of the machine and in which the sleeve slides. The shaft IUI has a threaded portion I08 which is engaged by a nut member I09, the nut member having a bore H formed therein by which it is slidably supported on an unthreaded portion Ill of the shaft IBI. The nut member has a gear II2 frictionall mounted thereon and forming part of the gear train 55 which is driven by the hydraulic motor 53.

The gear I I2 is mounted between two shoulders H3 and H4 for-med on the nut member and a friction plate I I5 is interposed between the gear I I2 and the shoulder I M and continuously urged into frictional engagement therewith by springs H6. A pin II'I serves to prevent relative rotational movement between the friction plate H5 and the gear I I2. It should now be apparent that the nut member is constantly driven :by the hydraulic motor 53 and at whatever speed the motor is set for and that the threaded portion or screw N38 is driven by the friction plate. Since the nut member is slidably mounted on the shaft 1 I05 any difference in speed between the rotation of the screw and nut will cause a relative axial shifting between the nut member and the shaft because the shaft is held in a substantiall fixed position axially by the friction roller 93. movement of the nut member is a function of the differential between the rates of rotation of the screw and of the nut.

Advantage is taken of this movement to effect or correct a change in the rate of rotation of the hydraulic motor. The first is deliberately pro duced while the second is automatically produced in response to a change in operating conditions in the machine. In either case let it be assumed that the screw and nut are rotating in the same direction and at the same speed with the result that no relative axial movement is occurring between them.

A change in rate is deliberately effected by rotating the pinion EM, thereby shifting the friction roller 93 radially of the disc 92, thus increasing or decreasing the rate of rotation of the disc 92 and connected screw I86. This immediately causes a relative axial shifting between the screw and nut which is utilized to operate the control valve El. This is accomplished by pivotally connecting a lever I I8 at I I9 to the valve plunger 61' and providing a ball-shaped end I on the lever us for engaging a groove l2I formed in the periphery of the nut member. The lever H8 is connected to the valve plunger at some point intermediate its length so that the other end of the lever can be pivotally connected at I22 to a link I23 which depends from a lug I 24 formed integral with the cylinder block 56. The link is pivotally connected to the Mg by a pin I25.

When the nut begins to move relative to the screw, it rotates the lever H8 about the pivot I22 causing movement of the valve plunger 61. This will shift the plunger off center and cause a pressure flow in either line 'H or II, thereby shifting the cylinder block 66. Since a slight delay will occur before the shifting of the cylinder block registers in the form of a change in rate of the gear 54, and since the nut is continuing Thus,

its movement, a feed back connection comprising the link I23 is provided so that as soon as the cylinder block begins to move it will cause a movement of the valve plunger in a direction opposite to that in which it was first shifted by rotating the lever II8 about the pivot I20, thereby tending to close or centralize the valve plunger 61. This serves as a sort of anticipating mechanism and prevents overrun of the cylinder block and thus reduces hunting in the sys The ratio of the arml I9i22 to the arm lit- 520 of the lever IIB is made preferably in approximately a 2-1 ratio whereby the valve movement effected by the nut is relatively slower than the valve movement effected by the cylinder block. Since the follow-up or anticipating movement effected by the cylinder block is faster than the original movement, the tendency to overrun is largely eliminated, which prevents oscillation from being set up. As the motor comes to the new required speed the nut slows down and finally stops when its speed matches the speed of the screw.

In the second case mentioned above, a change in rate may also be effected automatically by sudden increases or decreases in the cutting load which would be reflected in variation of the motor speed and thereby in rate changes of the nut relative to the constant speed of the screw. Readjustment of the motor speed would be brought about, however, in the same manner as previously explained.

It will now be evident that a variable feed mechanism is provided from which any feed rate may be selected, and that means are provided for automatically maintaining that rate regardless of changes in load on the machine.

The feed rate selecting mechanism is shown more particularly in Figures 4, 5, 6 and ll of the drawings to which reference may now be had. The pinion I00 shown in Figure 2 which, as previously explained, operates the shifter for adjusting the friction roller 93, is mounted on the end of a shaft I26 which shaft extends through the front wall I21 of the bed ii) for rotation by a dial I28 permanently secured to the end of the shaft. For convenience of rotation this dial has an operating knob I29 by which the dial may be rotated to align any of the feed rate indication graduations I38 on the plate i3i, Figure 11, with a fixed reference mark I 32 inscribed on a fixed part of the machine as shown in Figures 4 and 11.

Thus, any desired feed rate may be manually selected by means of this mechanism. The dial is frictionally held in any position by a friction mechanism comprising a spring pressed plunger I33 mounted in a socket of the plate I2! and engaging a fiat friction ring its which is carried by the dial.

Means have also been provided whereby this dial may be automatically adjusted to obtain a variable feed rate during a single stroke of the table. This is accomplished by providing a variable feed rate determining cam I35 which has a properly shaped contour in accordance with feed rate variations desired at different points in the table stroke and this plate is attached by T-bolts I36 mounted in a T-slot I 31 to the face of a chip and coolant receiver $38 which, in turn, is attached to the front of the table !2, the relationship being more clearly shown in Figure 8 of the drawings.

A follower roller I39 rides against the underside of the cam plate I35 and is rotatably supported by a shaft I40 attached to the upper end of a reciprocable slide I4I. As shown in Figure 4, this slide is connected through a link I52 and a bell crank I43 to a lever I44. A spring M5 has one end connected to a depending lug I45 formed on the lever I44 and the other end connected to a fixed pin I41 for exerting a constant urge on the lever in a direction to effect clockwise rotation of the bell crank I43 and thereby a continuous urge on the roller I39 into engagement with the underside of the cam.

The dial I28 has an arcuate shaped T-slot I48 formed therein for receiving a clamping screw I451 having a T-shaped head I58 riding in the slot. The screw passes through a bushing I5I formed in the end of the lever I44 and a knurled clamping nut I52 threaded on the end of the screw serves to operatively connect the lever I44 to the dial I28 while still permitting relative rotation of the lever with respect to the dial.

The vertical movement of the slide I-II is of limited extent and is not sufficient to effect rotation of the dial throughout its complete range of movement and therefore the adjustable connection of the lever I44 to the dial is provided to select a specified range of feed rates suitable to the operation in hand. When the automatic feed rate feature is not desired the knurled nut I52 may be loosened which thereby permits independent rotation of the dial.

The direction and rate of movement of the table is determined by the direction clutches 59 and 52, the rapid traverse clutch 43 and the feed clutch 16. All of these clutches are hydraulically operated clutches and are connected to a single control valve, various sections through which are shown in Figure 3 and indicated by reference numerals I53, I54, I55, I55 and I51. This valve has a rotatable plunger I58 which is connected by the gearing I58 to the operating handle I59 as shown in Figure 20, the handle being mounted on the front of the machine as shown in Figure 1 of the drawings.

In Figure 3 the handle is shown in a stop position and in addition to this it has four other positions, two of which are feed positions and two of which are rapid traverse positions. In other words, the lever is movable clockwise through an angle of 45 degrees to a feed left position indicated by the axis I50 and another 45 degrees to a rapid traverse left position indicated by the axis IIBI. It is also movable 45 degrees in a counterclockwise direction to a feed right position indicated by the axis I62, and another 45 degrees to a rapid traverse right position indicated by the axis I63. Thus, the lever has five different positions which means that the plunger I 59 may also assume five different positions.

The are connected by channels I54 and I55 to ports I55 and I531 of the valve section I53. The rapid traverse clutch 43 is connected by channel I 69 to port I18 of section I55 and the feed clutch 16 is connected by a channel I1I to port I12 of section I51. The plunger I 58 has an axial bore I13 which serves as a pressure supply channel and this here is intersected by a cross bore I14 formed in the periphery of the plunger and which is always in communication with ports I15 and I11. The port I15 is supplied through channel I18 which is branch connected at I19 to a direction determining clutches 58 and 52,

pilot pump supply line I that is maintained under pressure by a pump I 8|. This pump has an intake I82 through which fluid is withdrawn from a reservoir I83 through a channel I84 in which is serially arranged a filter I85.

The annular groove I 15 serves to maintain a constant pressure supply connection between the fixed ports I16 and I11 regardless of the rotatable position of the valve plunger whereby the bore I13 is always under pressure. The valve plunger is shown in a stop position and it will be noted from section I53 that the pressure bore I13 is connected to ports I66 and I61 whereby both of the direction clutches 5i! and 52 are operatively engaged which locks the table. The grooves I86 and I81 in section I55 and the grooves I88, I89, I90 and I9] in section I51 are all exhaust or reservoir grooves. From this it will be seen that the port I15 leading from the rapid traverse clutch 43 is connected to reservoir and that the port I12 leading from the feed clutch 15 is connected to reservoir whereby neither the forward nor the reverse gear trains are rotated.

Referring to section I51 of the rate and direction control valve, it will be noted that the valve has two cross bores I92 and I93 which intersect at right angles and also intersect the axial pressure bore I13 whereby when the handle I59 is rotated to the position I69 the pressure bore I93 registers with port I12, thereby admitting pressure to channe I1I to effect engagement of the feed clutch 16, or when the handle I59 is rotated to the position I62, the cross bore I92 registers with port I12 to effect the same result.

Thus, whether the handle I59 is rotated to the position I55 or the position I52 the feed clutch is caused to be engaged.

Referring to section I55 it will be noted that the plunger is provided with two segmental grooves I95 and I95 so that even although the plunger is rotated 45 degrees in either direction the port I10 remains connected to the reservoir groove I86 by means of the groove I94 whereby the rapid traverse clutch remains disengaged for either feed position. When the valve is rotated 90 degrees from the position shown to either of the rapid traverse positions I5I or I53 a cross pressure bore I96 registers with the port I15, thus admitting pressure to channel I55 to effect engagement of the rapid traverse clutch 43. At the same time either the reservoir groove I89 or the reservoir groove I9I is in registry with the port I12 providing for disengagement of the feed clutch 16 during rapid traverse.

As previously mentioned, when either the feed clutch or the rapid traverse clutch is engaged, the gears 45 and 43 are simultaneously driven in opposite directions and it is, therefore, necessary to disconnect one of the clutches associated therewith. This is accomplished as shown in section I53 of the valve by providing a reservoir port I 91 and a double intersecting segmental groove I93 whereby upon rotation of the valve plunger through 45 degrees counterclockwise the port IE5 is connected to the reservoir port I91 to release the pressure on direction clutch 55 while maintaining the pressure connection to the port I51, or if the valve is rotated clockwise the port I61 is connected to the reservoir port I 51 and the pressure connection is maintained to the port I55 whereby the clutch 52 is released and the clutch 55 is engaged. This same condition prevails even although the valve is rotated through another 45 degrees in either direction for rapid traverse purposes.

Thus, the portion of the valve at section I53 selects the direction of table movement regardless of whether a feed rate or a rapid traverse rate is desired. It will now be apparent that the lever I59 may be utilized to select the rate and direction of movement of the table and that these results are accomplished by providing four different positions for the lever as well as an intermediate stop position. This lever may, of course, be rotated by hand but for automatic cyclic operation of the machine it is necessary to provide additional means for effecting this rotation automatically. This is accomplished by providing a pinion I99 on the shaft I59 which supports the lever I59 as shown in Figures 12 and 13 and a reciprocating rack bar 200 in engagement with the pinion.

The rack plunger is slidably mounted in a control block 20H and is provided with a key 202 which slides in a spline 203 to hold the plunger against rotation and thereby maintain alignment of the rack teeth with the pinion. The rack plunger has a pair of circular discs 204 and 205 attached thereto in spaced relation and located on opposite sides of control block 20L The control block has four sets of operating plungers slidably mounted therein and spaced circumferentially about the rack plunger 200 and in such relation that they may engage the discs 204 and 205 for shifting purposes. A rolled-out view of these plungers is shown in Figure 3. They comprise a first pair of plungers 208 and 201, a second pair of plungers 20B and 2&9, a third pair of plungers 2H] and 2H and a fourth pair of plungers 2I2 and 2I3.

It will be noted that of each pair of plungers one is engagable with the plate 204 and the other with the plate 205. Each plunger has a piston head 2M which is slidable in a cylinder whereby upon admission of pressure to the cylinder the plunger may be shifted to effect axial movement of the rack plunger 200.

The sets of plungers are of different lengths and this is necessary in order to move the rack plunger different distances and thereby the valve to any one of its five different positions. The full line position of the plunger shown in Figure 3 represents the stop position from which the plunger is movable axially to two different posi tions above for feed and rapid traverse respectivel for one direction of table movement and to two different positions below for feed and rapid traverse respectively for the other direction of table movement. It will be noted that the plungers 2I2 and 2I3 are at the limit of their stroke and therefore are capable of moving the plunger from either of its two upper positions or its two lower positions to the central position shown.

It is, of course, necessary in starting the machine to manually move the lever I59 to one of its four operating positions after which any change or succession of changes may be made automatically.

The pair of feed plungers 2I0, 2II are utilized for shifting the control plunger from either one of its rapid traverse positions to one of its feed positions. The extreme upward or downward position of the rack plunger is the rapid traverse position, and if the plunger, for instance, is manually moved to its extreme upward position and the plunger 2 I was fluid actuated it would push the plunger downward to a feed position. Sim- 10 ilarly, if the rack plunger was moved downward to its rapid traverse position the plunger 2 would move it up to its feed position for the other direction. Therefore, these two plungers are made shorter than any of the other plungers.

The plungers 208 and 209 are utilized to produce the other effect of shifting the rack plunger from either feed position to a rapid traverse position. Since the rapid traverse position is the extreme position in either direction these two plungers are made longer than any of the other plungers.

In other words, if the rack plunger was in a feed position and the plunger 208 was hydraulically actuated, it would shift the control plunger 2% upward to its extreme position corresponding to rapid traverse in one direction. Similarly, the plunger 209 would operate to shift the control plunger 200 downward from a feed position to a rapid traverse position.

The plungers 205 and 201 are the reversing plungers and are made of such length that they can move the rack control plunger 200 from either a rapid traverse or a feed position for one direction of table movement to a feed position only for the opposite direction of table movement. In other words, whenever the table is reversed its new direction of movement will take place at a feed rate. If a rapid traverse rate is desired additional dogs must be set so as to effect operation of one of the rapid traverse plungers 208 or 209 after the feed rate has been established.

Fluid operation of these various operating plungers is controlled by a series of pilot valves in the form of trip plungers which are indicated by the reference numerals 2I5, 2I6, H1, H8, H9 and 220, which are arranged as shown in Figure '1. The plungers 2I5, 2I6, 2H1 and H8 are individual for control purposes to the plungers 206, 201, 208 and 209 respectively. The plungers 2I9 and 220 are so connected that they control operation of plungers 2I0, 2H, 2I2 and H3. The valve portion of plungers 2I5 and 2I6 have pressure ports HI and 222 respectively, exhaust ports 223 and 224 respectively and intermediate ports 225 and 226 respectively which are connected by channels 221 and 228 to the operating cylinders for the reversin plungers 206 and 201. The plungers 2!?) and 2I6 have annular grooves 229 and 230 formed therein which terminate in wide spools 23I and 232 at one end and narrow spools 233 and 234 at the other end.

Springs 235 act on the ends of the plungers to hold them in operating position, each plunger having a shoulder 236 which limits its movement by the spring. It will be noted that in the normal position of the plungers, which is that shown in Figure 3, the pressure ports 22I and 222 are closed by the spools 23I and. 232 and that the intermediate ports 225 and 226 are connected to the exhaust ports 223 and 224 respectively by the annular grooves 229 and 230. Thus, normally,

. there is no operating pressure on the reversing plungers 206 and 201. Should either of these plungers be depressed, however, by a suitable dog carried by the table the exhaust port will be disconnected by the proper spool, either 233 or 234, and a pressure port 22! or 222 will be connected to the respective intermediate port 225 or 220, thereby causing operation of one of the plungers 206 or 201. The exhaust ports 223 and 224 are connected to a common return line 231.

The next pair of plungers 2H and 2I3 have pressure ports 238 and 239 and-a pair of inter-: mediate ports 2% and which are connected by channels 262 and 243 to the operating cylinders for the rapid traverse plungers 2538 and Edd. The trip plungers 2 l l and 2 l 8 are provided with spools 25d and 2 respectively which are flanked by annular grooves to control the connection of ports 2 353 and 24], either with one of the pressure ports or with one of the exhaust grooves 256 or fidl. ing Edit and 249 to the common return line 23?. These plungers are also held in position by springs 235 and limited in their movement by shoulders 2%, When these plungers are in their normal position as shown in Figure 3 the ports 2% and are connected to exhaust as shown and when the plunger is moved downward the spools and 265 uncover the ports 2% and 284 sufiiciently to effect connection with the pressure ports 238 and 23$ respectively.

The pair of plungers ZIQ and 225 have ports 25d and 25! which are connected by channels 252 and 253 respectively to the operating cylinders for the feed plungers 2m and 2. They also have a pair of ports 254 and 2555 which are eventually connectible to the operating cylinders for the stop plungers 252 and M3. The plunger 213 has a pressure port 256 and the plunger 220 has a pressure port 25! which are connected to a common supply line 258.

Again, the plunger 22% has a port and the plunger 2l9 has a port Zfiil and these two ports are connected to a common line Ziil.

Attention is invited to the fact at this point that the pressure ports of the plungers Zi'l to 22d are so connected to pressure in accordance with the direction of movement of the table that certain of the plungers are effective during one direction of table movement, and the remaining plungers are effective during the other direction of table movement, the purpose of this being to obviate the necessity for using latch dogs. This may be characterized in a general way'as applying directional control to the trip plungers. The

application of directional control to these plungers is obtained in the following manner.

The channel 232 and its branch channel 258 terminate in a port 263 of the rate and direction control valve as shownin valve section 553. Similarly, the channel 2M and its branch Efii terminate in a port 265 also shown in section IE3. It will be noted that in the stop position of the rate and direction control valve that both of the ports 253 and 255 are connected to the exhaust port l9! and thereby through the common return line 237 to the reservoir I83. Thus, when the machine is stopped all of the plungers 2H to 22s inclusive are rendered ineffective if depressed by dogs. Although pressure is normally connected at all times to the reversing trip plungers 2 l5 and p 255, these plungers in their normal position connect the supply lines to the operating plungers 20d and 20'! to reservoir, from which it should now be evident that none of the operating cylinders 2 [4 have pressure in them when the machine is stopped and even although the machine would come to a stop position with a stop dog holding one of the plungers 259 or 228 down because even although that plunger is held down the operating pressure is disconnected therefrom by rotation of the control valve to the stop position. This movement is insured by providing a multiple detent plate 2%! on the shaft 159 as shown in Figures 12 and 13. This plate has a central notch 2002 which is engageable by a detent 29% pivoted on a These grooves are connected by interdrill- 2 Pi ndhe d sa n t h l by a sp in 2W5. Other notches 2605 and Zilfll are provided for the two feed positions and notches will) and 2;?99 for the rapid traverse positions. The purpose of this is that when the control lever E59 is manually thrown from its stop position to any of, its operating positions that it does not have to overcome pressure in any of the operating (3Y1? inders 2 Hi.

When the valve plunger I58 is rotated through an angle of 45 degrees in one direction from the position shown in "valve section I53 the port 2253 becomes connected to the pressure groove i 53, along with the port I whereby the ports 25,6, 25 and 238 are rendered active and the remaining ports 239, 259 and 26!] remain inactive. This condition still obtains should the valve plunger be rotated in the same direction to a rapid traverse position. When the valve is rotated counterclockwise irom the position shown the port 265 becomes connected to pressure along with the port 561 which new results in ports 255, 250 and 239 being rendered active and the remaining ports 238, 256 and 251 being rendered inactive. Thus, the valve I58 is enabled to apply directional control to the trip plungers in such a manner that if certain of the plungers are depressed during a given direction of table movement they are ineiTective for producing any change in the rate of table movement.

Continuing now with the operation of the trip plungers 2H3 and 2258, these plungers have spools 2I9' and 229' which are of such width and so located axially that upon a predetermined downward movement the pressure port 255 is connected to port 250 in the case of plunger 2 IE, or pressure port 259 is connected to port 25! in the case of plunger 220. In either case, this produces a. feed movement.

Upon further downward movement of plunger 2|9, port 256 is disconnected from port 258 and connected to port 254 to thereby efiect operation of the stop plunger 2E2. There will be no delay action because the delay plunger 238 is not actuated and therefore the ports 2% and Salt will remain interconnected.

Similarly, further downward movement of plunger 220 will interconnect port 258 with port 255 and thus effect actuation of plunger 253.

It. will be noted that due to directional control only one of the lines 258, 25! is under pressure at a time, which renders only one or the trip plungersv effective as a feed and stop plunger. However, there is a cross connection to the other plunger as at port 25.7 or 2&0 which serves to connect pressure to the other control plunger a Hi2 or 2|3. The purpose of this is to alternately supply pressure to the plungers in accordance with the direction of movement so that if a delay action is needed at reversal, the cylinders 214 will be full of fluid when the supply is cut off by the delay plungers 261, 268 now to be explained.

In reversing the direction of table movement it is oftendesired that the table dwell for a predetermined time after it has stopped, and before it starts its new direction of movement. This dwell is obtained by providing a delaying mechanism, which is indicated generally by the reference numeral 265 in Figure 3.

This mechanism comprises two delay plungers 2671 and 268 and a pair of delay throttle valves 269v and 219, there being one for each direction of movement. This makes it possible to provide a delay at one end of the table movement which is different than the delay at the other end of the enemas? '13 table movement. These are shown more fully in Figures 9 and 10.

One end of the cylinders 211 and 212 containing the plungers 261 and 268 are connected by branch lines 213 and 214 to channels 221 and 228 respectively whereby when either of these channels are under pressure the respective plunger will be shifted. The rate of shifting will depend upon the setting of the throttle valves. It will be noted that the pressure entering port 213 or 214 is capable of operating on the full diameter of the plungers, while at the other end the plungers have a reduced diameter which extends through the housing 215, thereby reducing the effective diameter at that end. The purpose of this is that the ports 216 and 211 which supply pressure to the reduced ends of the plungers are connected through channel 218 and port 111 of the rate and directional control valve to the same source of pressure that the ports 213 and 214 are connected so that by reducing the effective area at one end a pressure differential may be obtained for shifting the plungers.

The ports 216 and 211 are provided simply for the purpose of supplying fluid to the chambers 218' and 219, the fluid being forced out of these chambers by movement of the plungers through ports 280 and 281 which are connected to ports 282 and 283 of the throttle valves. The throttle valve plungers 269 and 210 are threaded in the housing 215 as shown at 284 and are provided With knurled operating knobs 285 and mounted on the front of the machine as shown in Figure 1. Each throttle valve plunger has a tapered portion 286 which is adjustable to variably throttle the ports 282 and 283 and the fluid passing through these ports returns to the supply line 218 through ports 281 and 288.

The method of obtaining a delayed reversal is accomplished by having a reversing plunger 206, or 201 as the case may be, shift the control plunger 200 to a stop position, preventing movement of the plunger 200 through the stop position by placing pressure in one of the operating cylinders for either plunger 212 or 213, and then releasing the pressure from these cylinders at a predetermined slow rate until the desired time of delay has been accomplished.

It will be recalled that all of the operating cylinders 214 are supplied from the same source of pressure and therefore in order to enable the plungers 212 or 213 to stop the movement of plunger 200 caused by actuation of the operating plungers 206 and 201 the diameters of the piston heads 289 and 290 are made larger than the diameter of the piston heads 291 and 292 of plungers 206 and 201 respectively. Thus, when the plunger 206 or 201 is hydraulically actuated it will shift the plunger until either the disc 204 or the disc 205 on plunger 200 engages the end of either plunger 212 or 213 depending upon the direction of actuation and then the plunger will stop. It must be remembered that while this part of the operation has been proceeding, the rate and direction control valve plunger 158 has been rotated from some position into the position shown in section 153. This would normally disconnect the pressure from the operating cylinders of pistons 212 and 213 if directly connected to the trip valve plungers 219 and 220. To obviate this they are connected through the plungers 261 and 268 in the following manner.

The ports 254 and 255 of the trip plungers 219 and 220 are connected through channels 293 and 294 to ports 295 and296 of the. delay plungers and when these plungers are in theirnormal posi tion, as shown, these two ports are connected by annular grooves 291 and 298 to ports: 299 and 300. These latter ports are connected by channels 301 and 302 to ports 303 and 304 of a spindle control valve 305, the purpose of which will be explained hereafter.

In the running position of this valve the ports 303 and 304 are connected to ports 306 and 301 and thereby through channels 308 and 309 to the operating cylinders for the plungers 212 and 213. It will be noted that the ports 295 and 296 are so positioned that immediately upon upward movement of either of plungers 261 and 268 these ports will be immediately closed, thereby trapping fluid in channels 301 and 302 while it is still under considerable pressure. This same movement will also close ports 216 and 211. The portion of the movement of plungers 261 and 268v which closes these four ports can take place immediately upon pressure entering either channel 221 or 228 due to actuation of the reverse valve plungers and therefore this portion of the move ment can be completed by the time that the rate and direction control valve plunger has been rotated to a stop position.

All of this results in the table coming to a stop which means that the dog which operated either the plunger 215 or 216 will stop in position to hold the plunger depressed whereby the pressure will still be maintained in either channel 221 or 228 to complete the further movement of the trip plunger which will terminate when either the annular groove 291 or 298 has been moved into such position that the ports 299 or 300 will be connected to exhaust ports 310 or 311. When this has happened the pressure will be released in the operating cylinders for plungers 212 and 213 permitting the operating plungers 206 or 201 to complete the additional movement of the control plunger 200 to its proper feed position.

It will thus be seen that when the table is reversed that it is first brought to a stop, a delay action is introduced and then the table is restarted in a new direction and that this is all accomplished automatically.

Duplicate manually operable controls have been provided for traversing the table and these are mounted on opposite sides of the bed for the convenience of the operator. Interlocks have been provided for rendering the manual controls inoperable during power operation of the table, while on the other hand when the manually operable controls are effective they render the reversing trip plungers 215 and 216 ineffective by disconnecting the operating pressure therefrom. Normally, the operating pressure is continuously connected to these plungers in order that they may rotate the rate and direction control valve through its neutral position. With the rate and direction control valve plunger in neutral position it will be obvious that if one of the reversing plungers should be accidentally engaged by a trip dog during manual traverse of the table that the plunger would be rotated to a feed position causing power operation of the table and since power operation is dominant as respects manual operation, the manually operable controls would be rendered ineffective and the table would continue to be moved by power, which condition is wholly undesirable.

The mechanism for effecting manual operation of the table comprises a shaft 312 which extends crosswise. of the bed. [0. and at either end is provided with a spur gear 313. At an intermediate point the shaft 3l2 is provided with a bevel gear 3| 4 which intermeshes with a bevel gear 3|5 mounted on the extended end of the shaft 25. The other end. of the shaft is directly connected to the gear 22 and thereby to-the table operating mechanism, and during power operation this shaft is rotated due to the engagement of the clutch 2? with the power driven gear 2 6".

Because of this, the spur gears 3l3 are rotated during power operation of the table. For manual operation axially shiftable spur gears 3l6 are mounted in the bed for engagement with the spur gears 3H3 but in order to prevent engagement during power operation interlock plungers 3|! are provided which normally hold the gears 315 out of mesh with the corresponding gears 3l3. These plungers are normally held in the position shown by springs3l 8. These plungers are slidable in cylinders 3l'9 and are provided with piston portions 320 whereby fluid pressure may be, connected to one end of the cylinders to effect retraction of the plungers when the rate and direction control valve is in a neutral position. This makes it possible then for the operator to axially shift the gear 3l6 into mesh with the gear 3&3 without any resistance. Should these two gears be left in mesh the hydraulic connections are such that pressure is relieved in the cylinders and the springs 3l8 immediately shift the gears 3? out of mesh and hold them against return movement until the table is stopped.

This automatic operation of the plungers is accomplished by providing the rate and direction control valve at section I56 with a diametrical pressure cross bore I95 which inthe stop position is in registry with port 32I'. This connects pressure to channel 322 which has branch connections 323' and 324 to the ends of the respective cylinders-3| 9. When the rate and direction control valve is rotated through 45' degrees' in either direction it will be obvious that the port 32| is connected to exhaust, thereby relieving the pressure in the cylinders 315' whereby the springs 3H5 may become effective.

The gears 355 are mounted on the ends of short shafts 325 and each shaft is provided withan annular groove 326' which may be utilized as a valve for controlling the connection of pressure to the reversing trip plungers H and 11 61 Tothis end the bore 321 in which the shaft slides is provided with three ports 328, 329' and 330. The port 328 is connected by channel 33lto the supply line. Etc. The port 328 is thus a constant pressure port and is connected by the annular groove 326 to the port 329 when the gear 3H3 is disengaged whereby fluid pressure flows through the line 332 to port 333 of the other control shaft 334. 7

When this shaft is in an inoperative position the port 333 is. connected by the annular groove 325 to port 335 and thereby to channel 333 which leads to the pressure ports 22! and 222 of thereverse trip plungers 2 l5 and 256. It will thus be seen that the supply pressure for the trip plungers is serially connected through the two manually operable devices whereby if either one is shifted to. an operative position either the port 325; or the port 333 will be closed to disconnect the supply pressure to the trip plunger-s.

The channel 336 is provided with a branch 331 which leads to port 338 in the cylinder 33 of the power disconnect clutch 2!- whereby this clutch is held in engagement whenever the manual controls are in an inoperative position. The real purpose of this clutch is to disconnect the'power drive mechanism from the shaft 25 during manual rotation so that all of the power driven gearing does not have to be rotated manually during manual traverse of the table. When either of the shafts 325 or 334 is shifted for manual operation the port 329 is connected to the exhaust port 333 or the port 335 is connected to an exhaust port 339 which thereby makes it possible for fluid to escape from line 336 and permit shifting of clutch 21.

The various trip plungers are reciprocably mounted in a trip plunger valve block 340 attached as a unit to the top of the bed I!) in front of the table as shown in Figures '7 and 8. Referring to Figure 7, the two reverse plungers 2 I5 and 2H5 are located at the front furthest from the table, the feed and stop plungers 2!!! and 220 located nearest the table, and the rapid traverse plungers 2|? and 218 located in between. The contact portions on the tops of the .plungers have been so aligned that operating dogs for one direction of movement will not contact or i-dly depress any plunger except the one for which it is particularly design-ed. For instance, the rapid traverse plungers 25 l and 218 are provided with wedge-shaped operating portions 34! and 342 re-' spectively and these lie in separate planes for engagement by trip dogs 343 and 344 respectively. The stop dog 345 and the feed dog 346 are adapted to engage the front wedge-shaped operating portion 34! of plunger 225, while the stop dog 348 and feed dog 34.) are adapted to engage the central operating portion 350 of trip plunger 2l9.

The rear operating portion .35l of plunger 22!) and the rear operating portion 352 of plunger 2 l 9 lie in the same plane and are engageable by fixed safet dogs 353 located at extreme ends of the dog carrying. structure and are only effective if the table should overrun its range. of movement. The reversing dogs 354 and 355 lie in the same plane as the operating portions 356 on the reverse lplungers H5 and 2| 5 and these are arranged in thev same plane because either of the trip dogs cannot. go beyond its particular plunger due to the fact that depression of the plunger causes reverse movement of the table.

' All o the trip dogs are mounted on the underside of the chip and coolant receiver I38 which is attachedto the front of the table as shown in Figure 8. The method of attachment comprises the formation of a dovetailed guide 3.5! on the bottom of the receiver and providing each of the dogs with a corresponding formation to slide on this guide one guide portion 358 of each dog being made separate so that a clamp screw 359v may be utilized for clampin the dog in position or for slightly loosening it so that the dog may be slid to a new position.

It is, of course, necessary to remove the screw altogether if the dog is to be removed from the dovetailed guide. Each dog has an upper bearing surface 359 which bears against an established surface 360 formed on the bottom of the receiver at a definite height above the tops of the operating plungers. This makes it possible to establish a standard dimension for the height of the operating portion of the dog with the exception of the dogs for the feed and stop plungers which must be of diiferent height because the plunger has two difierent positions as previously" explained' In other words the stop plunger-is made the same-- height as the remaining plungers but--tlie- :feed-= dogs are made lessin height because a shorter movement of the plunger is all that is necessary to effect operation of the feedplunger.- The height of these plungers hasbeen-diagrammatically illustrated in Figure- 3 from which it will be seen that the feed control dog does not extend down asfar as the remaining trlpid-ogsa It will be understoodthat the arrangementof dogs shown in Figure-7 is merely'illustrative-to show the relationship of-the pnrticular-dogswith respect to the trip-plungers "with =which= they cooperate and is not in any senseto be considered as limiting or-as showing-a set-upjor-a particular operating cycle; It will beunderstood that these" dogs may be rearranged-or evensome removed in: accordance with :the cycleto be performed on the machine and which procedure is clearly under-r stood. by those experienced in-theart. I

The spindle 'controltvalvey -iloi previously -re-- ferred to "has a rotatable =-plunger 4 provided-* with a; controller er 41%.- This le'verxhas three positions: It is shown -in-itscontrol or run posi tion in Figure 11 and isrotatable' from-this-posi-- tion to a stop-position.indicated-byline442 and to an automatic controlposition indicated lby line; In'its run position itinterconnectslines:30|' with 398', and 302 with 309*as shown in sections- 436 and 431' of the-valve.

In section-43V of-this-valve-there is-a pressure port 332 which is always inwcommunication with an'annular groove433 to keep it-under pressure.v

A pair of longitudinally extending; grooves 434 and 635' intersect the annularpressure-grooveflis andextend through sections 436: and 431 ofth'evalve whereby when the Valve is rotated to its-stopposition the pressure groove 434 is connected. to

lines 338 and 3fi9'to effect shifting of the table control plunger 200 to a stop position. When the" valve is rotatedto its automatic position" it does t not change the connections established in...the: runpositiom The valve plunger has a secondwpair 'oflongi1- tudinally-extending grooves 43.8 and 439 which run from the annular pressure groove 433' to section 440 of the valver This section-mas a port 425%- which is connectedbychannel 428 to a pressure operated switch "391* for "a spindle dri'ving motor. A pair of leads-398 and 4D I extendgfrom this s'witch to suitable-control mechanism for this purpose, but this mechanismiforms no :part" of the present" invention but'is' showniand described in copending divisional-application, Serial No. 681,854, filed July 8, 1946: Suffice, it to say that when the valve is in its. run position-as shown in Figure ll, the pressure switch'is actuated to cause driving of the spindlaand when the sion in which *therate --may be steplessl'y varied and once the rate is determined, itis automath cally; maintained "regardless of. variation in load which. normally would "tend ytog vary the rate. These .featuresare combined in a single mech-- anism which may also be connected ior automaticvad'j ustmentby a feed rate control cam Itwill also be noted that an improved and efiicient'trip control mechanism mounted- :on the table;

hasbeen provided for the table transmission and which 'is .so. designed that latchdogsare :not

tween the supports atdifferent rates including a...

feed clutch,fa rapid traverse clutch, a final motiontransmitting train, means to selectively engage said" clutches for actuation. of, the train, a. con-.

-stant speed prime mover. for driving the rapid.

traverse: clutch, a variable speed. transmission, for: driving the .feed clutch including a pumpv driven by said prime mover, a variable displacementmotor, channels interconnecting said pumn.

-for actuation of'said motonmeans for varying. the displacement. .of; said ,motor,. a. drive train. from themotoli t0 the feed clutch, branch trains.

driven by the prime mover andthe drive train... respectively and terminating inlopposed relation.

to one anothenand means .to measure the speed differential between said. branch. trainslto efiect adjustment of .saidimotor. displacement until said differential .has. been, eliminated.

2. In' a machine tool. having. awork support and; 1-, l suDDQ11t,the. combination of transmis-.

sioh means for efiectingrelative movementbetweenthe. s.upports...at. different rates including. a feed. clutch, a rapid traverse. clutch, a finalmoa.

tion transmittingtrain, means to-selectively 8n:-

ga ecsaid clutches .for. actuation. of, the train, a constant speed prime mover for driving. the rapid traverse: clutch, a variable .speedtransmission.

iortdriv-ing the-.feeda clutch 'includingga pump:

drivemby saidprime mover; a variable; displace- 0 ment motor; 1 channels interconnecting, said. pump.

valve is rotated. to a stop position the port. 428

is connected to exhaust line.23'1 and the pressure switch is'released to stop the spindle.

When the valve is rotated to its automatic. position the. port 429 is connectedto. a lo'ngitudi nally extending groove M411formed inthe periphery of the valve plungen. and'thisi groove extends from section 440' to section 441" where it" intersects an annular groove. that '-is;,a1.way in communication withport 4452'. This latter port is connected to channel IH which is the; control line for the feed clutch 16 aspreviously described is automatically actuatem" There-has thus been-provided'a millingmachine having an improved and simplified Ieedtransmis 7.0 so that whenever line I H. is-under pressure it will be obvious that the spindle control pressure switch for actuationyot said .motor,,-means for; varying the displacement-of said motor, a drive train fromthe. motor; to; the feed: .clutch=,.branch trains driven. bytheprime mover and theudrive trainrespec tiv'ely-an'd. terminating intopposed. relation-to one another, means to measure thespeed diiferential between said branch trains: t'o eifiectadjustment of said motor displacement until said differential .has:been eliminated; and variable speed means in 011E? said branchtransmissions to var-y the output thereofand-=therebythe rate of-said motor. 3; In a -mi'lling "machine having a work sup-- port and a toolsupport; the combination of trans.-

missior-r-means foreifecting relative .movement between the supports at rapid traverse. and feed ing rates including; a rapid traverse train, a feed? train,-aconstant speed prime: mover for driving said rapid traverse train, a pump driven. by said prime mover; "a variable displacement hydraulic. motor actuated by said pump, means for operativel'y connecting the motor to the .feed train, v

means fo'r'varying the displacement oi'said motor and thereby varying the feed rate, andfluid op-.. erableclutches for selectively connecting either 19 of saidtrains for effecting said relative movement.

4. In a machine tool having a work support and a tool support, the combination of transmission means for effecting relative movement between said supports at rapid traverse and feeding rates including a feed gear and a rapid traverse gear, a constant speed prime mover for driving said rapid traverse gear, a pump driven by said prime mover, a variable displacement motor actuated by said pump, a pair of oppositely rotatable coaxial gears, means operatively connecting one of said gears for rotation by the prime mover at a constant rate, means operatively connecting the other gear for rotation by the variable displacement motor at a rate which is equal to said constant rate when the motor is set for maximum displacement, a third gear intermeshing with said pair of gears and operatively connected for rotation of the feed gear, and means to decrease the displacement of the pump to increase the rate of rotation of the feed gear.

5. In a machine tool having a work support and a tool support, a variable feed transmission for effecting a feeding movement between the supports including a fluid operable variable displacement motor, a diiferential mechanism including a first gear driven at a constant speed, a second gear driven by said motor, a third gear intermeshing with the first-named gears and operatively connected for effecting said feeding movement, and control means to vary the displacement of said motor including coaxial rotatable members one of which is driven by said motor, means for driving the other member at variable speeds, and means responsive to differences in the rate of rotation of said members for automatically adjusting the displacement of said motor.

6. In a machine tool having a work support and a tool support, the combination of transmission means for effecting relative movement between the supports including a feed transmission, a rapid traverse transmission, intermediate gearing, fluid operable clutches for connecting the respective transmissions to said gearing, a final drive train, a pair of reverse gears driven in opposite directions by said gearing, fluid operable clutches for alternately connecting the respective reverse gears to the final train, a source of pressure, selector means for coupling said pressure in various combinations to said clutches to determine the rate and direction of relative movement between said supports, said selector having another position for disconnecting pressure from the first pair of clutches and connecting pressure to said second pair of clutches to lock the final drive train against inadvertent movement when power is disconnected therefrom.

'7. In a machine tool having a work support and a tool support, the combination of means for effecting relative movement between the supports including a final shaft connected to the movable support, feed and rapid traverse transmissions, an intermediate shaft, means for selectively connecting said transmissions to said intermediate shaft, a selector clutch for connecting said intermediate shaft to the final shaft, manually operable means for rotating the final shaft including a shiftable member having an operating and a non-operating position, and means controlled by said member when in a non-operating position to efiect engagement of said clutch and when in an operating position to effect disengagement of said clutch.

8. In a milling machine having a work support and a tool support, the combination of transmission means for effecting relative movement between the supports including a feed and a rapid traverse clutch, a pair of reversing clutches, fluid operable means for shifting said clutches, a source of pressure, a multiposition control valve for connecting said source of pressure selectively to said clutches, a control rod for positioning said valve, a pair of oppositely acting hydraulic plungers for shifting said rod to a central or stop position, a second pair of plungers alternately operable for shifting said rod to one of its feed positions located on opposite sides of its stop position, additional fluid operable means for shifting said rod beyond its feed position to efiect rapid traverse, and another set of plungers for shifting said control rod from any of its positions on one side of its stop position to a feed position on the other side thereof.

9. In a milling machine having a work support and a tool support, the combination of transmission means for effecting relative movement between the supports including a feed and a rapid traverse clutch, a pair of direction determining clutches, fluid operable means for shifting said clutches, a source of pressure, a multiposition control valve for connecting said source of pressure selectively to said clutches, a control rod for pcsitioning said valve, a pair of opposed hydraulically actuated plungers for shifting said rod to a central or stop position, a second pair of plungers alternately operable for shifting said rod to one of its feed positions located on opposite sides of its stop position, additional fluid operable means ior shifting said plunger an additional distance to eflect rapid traverse, another set of plungers for shifting said control plunger from any of its positions on one side of its stop position to a feed position on the other side thereof, and means to stop and delay the movement of the control rod when it reaches its central position.

10. In a machine tool having a work support and a tool support, the combination of means for eifecting a relative feeding movement between said supports including a fluid operable variable displacement motor, fluid operable control means for varying the displacement of said motor including a control valve, a speed matching mechanism including a first rotatable member, independent means for driving said member including an adjustable rate variator which may be set to determine the support feed rate desired, a, second member in threaded engagement with the first and driven by said motor, and means to match the speed of the second member with that of the first member including an operative connection between said second member and said control valve whereby any bodily movement of said second member due to differences in rate with respect to the first member will cause actuation of said valve and thereby displacement adjustment of said motor.

11. ,In a machine tool having a Work support and a tool support, the combination of means for effecting a, relative feeding movement between said supports incllldin-g a fluid operable variable displacement motor, fluid operable control means for varying the displacement of said motor including a control valve, a speed matching mechanism including a first rotatable member, independent means for driving said member including an adjustable rate variator which may be setto determine the support feed rate desired, a second member in threaded engage ment with the firstandkdrivenwby said motor,"

means to match the speed of the secondmember with that of the first member'including anoperative connection 'between said second member and said control valvewhereby any bodily move ment of said second member due'todifi'erences in rate with respect to the first member will cause actuation of said valve and thereby displacement adjustment of said motor, and manually operable means for adjusting saidarate variator to increase or decrease the rate of rotation of said first member and thereby through said speed matching mechanism efiect a corresponding increase or decrease in the rate of rotation ofsaid motor and thereby a change in-the feeding rate of said support.

12. In a machine tool having a work support and a tool support, the combination of 'means for effecting a relative feeding-movement between said supports including a fluid-operable variable displacement motor, fluid operable control means for varying the displacement of said motor including a control valve,'a: speed matching mechanism including a, first rotatablemember, independent means for driving said member including an adjustable rate variatoriwhich may be set to determine the support feed rate desired,

a second member in threadednengagement with the first and driven by saidmotor; means to match the speed of the second member withthat of :the first member including an operative connection between said second member 'and said control valve whereby any bodily movement of said second member due to differences in'rate with respect to the first member will cause actuation of said valve and thereby displacement adjustment of said motor, a feed rate control cam carried by the movable support,-a plungercyieldingl held into engagement with said cam, and meansoperatively connecting said plunger With'said rate variator to effect automatic adjustment thereof.

13. In a machine tool having a work support and a tool support, the combination'of means for effecting a relative feeding movement between said supports including a fluid operable-variable displacement motor, fluid operable' control means for varying the displacement-of said motor ineluding a control valve, a speed matching mechanism including a first rotatable member, independent means for drivingsaidmember including an adjustable rate variator-which maybe set to determine the support 'feed rate desired, a-secnd member in threaded engagement with the first and driven by saidmotor, means tomatch the speed of the second member with that of the first member including an operative connection between said second member and said control valve wherebyanybodily movement of said i second member due to differencesin rate with respect to the first member-will cause actuation of said valve and therebydisplacement adjustment of said motor, a feed control cam carried by the movable support, a plunger yieldingly held into engagement with said-cam,means operatively connecting said plunger 'WifihvStidlEtbG variator to effect automatic 'adjustment thereof,

said connecting means including a link and a crank disc, a bell crank connecting-said link to the plunger, said link having a limited movement, and means to operatively connect the link to said disc at various circumferentially spaced points whereby various ranges of-feedrates maybe selected.

14. In a machine-:toolphaving aicvvork isupportw and a tool support,- the i combination? or trans mission: means for effectingrelative'movement.

between said supports including a variabledisplacement motor for eifecting feeding movements at various rates, said variable. displacement motor having a prescribed minimum speed, a differential mechanism comprising a pair I of co-axi-al gears and an intermeshing gear; means to couple the motor for actuation of one of said co-aXial gears, means to drive the other co-axial gear at a constant speed which is equal to the prescribed minimum speed of the first gear whereby the output speed of the differential may begin at zero.

15. In a transmission and control mechanism for the work support of a machine tool; the combination of a feed transmission, a rapid traverse transmission, means for selectively connecting said transmissions for movement of the table, a variable displacement hydraulic motor for driving the feed transmission, a constant clelivery pump for supplying fluid: to said motor, a monitoring mechanism for controlling the displacement or said pump for maintaining the out-- put speed of said motor constant under varying load, said mechanism also being adjustable to increase or decrease the rate of said motor, a prime mover, a first branch train'for driving the rapid traverse transmission, a second branch train for driving the pump, a third branch train for driving the monitoring mechanism, and means connecting all of said trainsfor actuation by the prime mover.

16. In a transmission and control mechanism for the work support of a machine tool, the combination of a feed transmission, a rapid traverse transmission, means for selectively connecting said transmissions for movement. of the table, a variable displacement hydraulic motor, a first gear driven thereby, a second gearco-axial with the first and rotatable at a constant speed, a third intermeshing gear coupled to the feed transmission, a constant delivery pump for supplying fiuid to said motor, a monitoring mechanism for controlling the displacement of said pump and thereby maintaining the output speed of said motor constant under varying load, said mechanism also being adjustable to increase or tie-- crease the rate of said motor, a prime mover, a first branch train for driving the rapid traverse transmission, a second branch train for driving the pump, a third branch train for driving the monitoring mechanism, a fourth branch train for drivingsaid second gear, and means connecting all of trains for actuation by the prime mover.

17. In a machine tool having a Work support and a tool support, the combination of transmission means for effecting relative movement between the supports at different ratesincluding a feed clutch, a rapid traverse clutch, a final motion transmitting train, means to selectively engage said clutches for actuation of the train, a constant speed prime mover for driving the rapid traverse clutch, a variable speed hydraulic transmission for driving the feed clutch, means for varying the speed of said transmission, a drive train from the transmission to the feed clutch, branch trains driven by the prime mover and the drive train respectively and terminating in opposed relation to one another, and means responsive to the speed differential between said branch trains to effect automatic rate adjustment of said hydraulic transmission to eliminate said differential.

18. In a machine tool having atwork support and a tool support, the combination of transmission means for effecting relative movement between said supports at rapid traverse and feeding rates including a feed gear and a rapid traverse gear, a constant speed prime mover for driving said rapid traverse gear, a pump and motor connected together in a closed circuit, the displacement of one of which is variable, means to drive the pump from said prime mover, a pair of oppositely rotatable co-aXial gears, means operatively connecting one of said gears for rotation by the prime mover in one direction at a constant rate, means operatively connecting the other gear for rotation by said hydraulic motor in the opposite direction at a rate equal to said constant rate when said displacement is set for a minimum rate, a differential gear intermeshing with said pair of gears and operatively connected for rotation of the feed gear, and means to vary said displacement to increase the rate of rotation of the feed ear.

19. In a machine tool having a work support and a tool support, the combination of a variable feed transmission for effecting a relative feeding movement between said supports including a constant displacement pump and a variable displacement motor interconnected in a closed circuit, means to control the displacement of said motor including a pair of interengaging rotatable threaded members, one of which is a monitoring member, power operable means to drive the monitoring member at variable rates, means to drive the other member from the motor, an actuator shiftable in response to variations in the rates of rotation of said members, fluid operable means for varying the displacement of said motor, and control valve means operatively connected to said actuator and shiftable thereby to reversely connect a source of hydraulic pressure to effect opposite adjustment of the displacement varying means for said motor.

20. In a machine tool having a work support and a tool support, the combination of a variable feed transmission for effecting a relative feeding movement between said supports including a constant displacement pump and a variable displacement motor interconnected in a closed circuit, means to control the displacement of said motor including a pair of interengaging rotatable threaded members, one of which is a monitoring member, means to drive the monitoring member at variable rates to determine the relative feeding rate between said supports, means to drive the other member from the motor, an actuator shiftable in response to variations in the rates of rotation of said members, fluid operable means for varying the displacement of said motor, control valve means operatively connected to said actuator and shiftable thereby to reversely connect a source of hydraulic pressure to effect opposite adjustment of the displacement varying means for said motor, and a feed back connection from said motor to said valves.

21. In a milling machine having a work support and a tool support, the combination of a variable hydraulic transmission for effecting relative movement between the supports, means to vary the output of said transmission over a range from a prescribed low speed to a prescribed maximum speed, a differential mechanism, means to drive one leg of said mechanism at a prescribed speed equal to the prescribed constant low speed of said hydraulic transmission, means to drive the other leg of said diiferentialirom said hydraulic transmission whereby when said hydraulic transmission is adjusted to its prescribed low speed the output of said differential is zero speed,

means to connect said output to a movable support, and means to increase the rate of said hydraulic transmission up to its maximum rate whereby the range of rates of movement of said movable support is equal to the difference between the prescribed minimum speed and the prescribed maximum speed of said hydraulic transmission.

22. In a machine tool having a work support and a tool support, the combination of means for effectin a relative feeding movement between said supports including a hydraulic transmission having an adjustable rate variator to determine the feed rate desired, a feed rate control cam carried by the movable support, a plunger yieldingly held into engagement with said cam, means operatively connecting said plunger with said rate variator to effect adjustment thereof, said connecting means including a link and a crank disc, a bell crank connecting said link to the plunger, said link having a limited movement, and means to operatively connect the link to said disc at various circumferential spaced points whereby various ranges of feed rates may be selected.

23. In a milling machine having a work support and a tool support, the combination of transmission means for effecting relative movement between the supports including a feed clutch, a rapid traverse clutch, a pair of reversing clutches, forward and reverse gearing between said clutches, fluid operable means for shifting said clutches, a source of pressure, a multiposition control valve for selectively connecting pressure to said clutches, said valve having a neutral position for connecting pressure to both of said reversing clutches to lock the movable support against movement, a feed position on one side of said neutral position for connecting pressure to the feed clutch and one of said reversing clutches, a second feed position on the opposite side of said neutral position for engaging the feed clutch and the other of said reversing clutches, a first rapid traverse position on one side of said neutral position and beyond the feed position for effecting engagement of the rapid traverse clutch and one of said reversing clutches, and a second rapid traverse position on the opposite side of said neutral position and beyond said second-named feed position for connecting pressure to the rapid traverse clutch and to the other of said reversing clutches.

24. In a milling machine having a work support and a tool support, the combination of transmission means for effecting relative movement between the supports including a feed clutch, a rapid traverse clutch and a pair of reversing clutches, fluid operable means for shifting said clutches, a multi-position control valve for selectively connecting pressure to said fluid operable means in different combinations, said valve having a neutral position, feed and rapid traverse positions on one side of said neutral position for one direction of movement, feed and rapid traverse positions on the other side of said neutral position for the other direction of movement, a first set of dog-operated plungers operatively connected for automatically shifting the valve between the positions on one side of said neutral position, a second set of plungers for automatically shifting the valve While on the other side of said neutral position, manually operable means for shifting the valve from its neutral position to one of its operative positions to start relative movement between the supports, and means siecedes? multaneously operable "bythe valve toconnect "'pressure'to one 'set'of 'plungers and disconnect .pressure fromthe'other' whereby only one set "bf plungers'is'eifective during a given direction of relative movement.

25. In'"a' milling" machine having a work' supfor one direction of movement on one side of said neutral position, a second pair of rate positions for the other direction of movement on the other side of said neutral position, a first dog-operated means for shifting said valve between one set of rate positions, another dogoperated means for shifting the valve between the other set of rate positions and a third dogoperated means for shifting the valve from either rate position on one side of said neutral position to a rate position on the other side of said neutral position.

26. In a milling machine having a work support and a tool support, the combination of trans mission means for effecting relative movement between the supports including a feed clutch, a rapid traverse clutch and a pair of reversing clutches, fluid operable means for shifting said clutches, a multi-position control valve for selectively connecting pressure to said clutches having a neutral position, a pair of rate positions for one direction of movement on one side of said neutral position, a second pair of rate positions for the other direction of movement on the other side of said neutral position, a first dog-operated if:

means for shifting said valve between one set of rate positions, another dog-operated means for shifting the valve between the other set of rate positions, a third dog-operated means for shifting the valve from either of its rate positions on one side of said neutral position to a rate position on the other side of said neutral position, and either of said first two-mentioned dogoperated means also being effective to shift the valve from either of its rate positions to a stop position.

27. In a milling machine having a work support and a tool support, the combination of transmission means for effectingrrelative movement between the supports including a feed clutch, a rapid traverse clutch and a pair of reversing clutches, fluid operable means for controlling the shifting of said clutches including a first set of dog-operated plungers for controlling the shifting of the feed and rapid traverse clutches, a second set of dog-operated plungers for controlling the shifting of the feed and rapid traverse clutches, means for determining the direction of movement of the support and simultaneously selectively connecting pressure to one or the other of said sets of plungers whereby the trip dogs that control the rate changes in one direction are ineffective during the other direction of support movement.

28. In a milling machine having a work support and a tool support, the combination of transmission means for effecting relative movement between the supports including feed and rapid traverse clutches, a pair of reversing clutches, means to control the shifting of said clutches "including" a multi-position control valve having "a"neu'tra1 position and operative positions on opposite sides thereof,'manu' a1 means for positioriing said valve in one of said operative posi- 'tions, apair of dog-operated reversing plunge'rs,

means effective upon operation of one of said plungersto effect disengagement of the feed and rapid'traverse clutches, engagement of both of said reversing clutches to brake the slide movement and subsequently effect engagement of the "feed clutch and one of said reversing clutches.

29. In a machine tool having a work support and a tool support, the combination of transmission meansfor effecting relative movement between the supports including a variabledis- W placement hydraulic 1 motor having a displacement regulator, means coupling the motor for effecting said relative movement at variable feed rates in accordance with the position of said regulator, means to control the position of said regulator including a pair of interengaging rotatably threaded members, one of which is a monitoring member, means to drive the monitoring member at variable rates, means to drive the other member from said motor, and means including a lever movable in response to variations in the rates of rotation of said members to adjust said regulator in a manner to cause the rate of the motor to conform to the rate of the monitoring member and a feed back connection from the regulator to said lever to modify the adjustment thereof.

30. In a machine tool having a Work support and a tool support, the combination of means for effecting a relative feeding movement between said supports at variable rates including a variable displacement feed motor, a displacement regulator therefor, a motion transmitting train coupling the motor to the movable support, means to control the displacement of said mot-or including interthreaded screw and nut members, means to connect one of said members for rotation by the motor, a monitoring mechanism for driving the other member in the same direction whereby when the speeds are equal no relative bodily movement will take place between said threaded members, means to increase or decrease the speed of the monitoring member, and actuating means responsive to ensuing bodily movement between said threaded members to adjust said displacement regulator to increase or decrease the motor rate until the motor speed matches the speed of the monitoring mechanism, and a feed back connection from said regulator to said actuating means to modify the effect of the latter.

31. In a milling machine having a work support and a tool support, the combination of a variable hydraulic transmission for eifecting relative movement between the supports, means to vary the output of said transmission over a range from a prescribed low speed to a prescribed maximum speed, a differential mechanism, means to drive one leg of said mechanism at a prescribed constant speed equal to the prescribed low speed of said hydraulic transmission, means to drive the other leg of said differential from said hydraulic transmission whereby when said hydraulic transmission is adjusted to its prescribed low speed the output of said differential is zero speed, means to adjust said transmission above its prescribed low speed to obtain low o erating speeds of high torque, means to connect the output of said hydraulic transmission to the feed side of a feed rapid traverse clutch, a rapid traverse transmission for actuating the rapid traverse 27 side of said clutch, and a pair of gears adapted to be oppositely driven by said clutch at either a feed rate or a rapid traverse rate, and means to selectively connect said last-named gears for opposite'directions of actuations of one of said supports.

ERWIN G. ROEHM. HANS FRITSCHI.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Name Date La Ducer Aug. 31, 1926 Number Number 

